KR101755476B1 - Planetary gear train of automatic transmission for vehicles - Google Patents

Abstract

A planetary gear train of a vehicular transmission is disclosed. A planetary gear train of an automatic transmission for a vehicle according to an embodiment of the present invention includes an input shaft receiving power of an engine; An output shaft for outputting the shifted power; A first planetary gear set having first, second and third rotating elements; A second planetary gear set having fourth, fifth and sixth rotating elements; A third planetary gear set having seventh, eighth and ninth rotary elements; And six control elements disposed at a portion for selectively connecting the rotary element and the rotary element, wherein the first rotary element and the seventh rotary element are connected to each other, ; A second rotating shaft including the second rotating element and the sixth rotating element, the second rotating shaft being selectively connected to the first rotating shaft; A third rotating shaft including the third rotating element; A fourth rotary shaft including the fourth rotary element and directly connected to the transmission housing; A fifth rotary shaft including the fifth rotary element and selectively connected to the input shaft or the fourth rotary shaft; A sixth rotary shaft including the eighth rotary element and directly connected to the output shaft; And a seventh rotary shaft including the ninth rotary element and being selectively connected to the third rotary shaft or the fifth rotary shaft. The planetary gear train of the vehicular automatic transmission may be provided.

Description

BACKGROUND OF THE INVENTION 1. Field of the Invention [0001] The present invention relates to a planetary gear train of an automatic transmission,

The present invention relates to an automatic transmission for a vehicle, and more particularly, to a vehicle automatic transmission capable of improving the fuel economy according to multiple shoes by implementing eight forward speeds with a minimum configuration and using the operating point of the low RPM region to improve the constant- To a planetary gear train of a transmission.

The recent rise in oil prices is causing infinite competition to improve fuel efficiency.

As a result, studies have been made to reduce the weight and reduce fuel consumption through downsizing of the engine, and in the case of the automatic transmission, studies that can secure both driving performance and fuel economy competitiveness through multi- .

However, the number of internal parts increases as the speed change stage of the automatic transmission increases, so that the mountability, production cost, weight, and transmission efficiency may be deteriorated.

Therefore, it is important to develop a planetary gear train that can maximize efficiency with fewer parts in order to increase fuel efficiency improvement through multi-shoe.

In this respect, an 8-speed automatic transmission is currently being applied to a real vehicle, and research and development of a planetary gear train capable of realizing a shift speed higher than that have been actively conducted.

The matters described in the background section are intended to enhance the understanding of the background of the invention and may include matters not previously known to those skilled in the art.

The embodiment of the present invention is a vehicle automatic transmission capable of improving the fuel economy according to the multi-shoe and improving the cruise speed of the vehicle by using the operating point of the low RPM region by implementing the forward speeds of the forward 8th speed and the reverse 1 speed To provide a planetary gear train.

In one or more embodiments of the present invention, the input shaft receives power from the engine; An output shaft for outputting the shifted power; A first planetary gear set having first, second and third rotating elements; A second planetary gear set having fourth, fifth and sixth rotating elements; A third planetary gear set having seventh, eighth and ninth rotary elements; And six control elements disposed at a portion for selectively connecting the rotary element and the rotary element, wherein the first rotary element and the seventh rotary element are connected to each other, ; A second rotating shaft including the second rotating element and the sixth rotating element, the second rotating shaft being selectively connected to the first rotating shaft; A third rotating shaft including the third rotating element; A fourth rotary shaft including the fourth rotary element and directly connected to the transmission housing; A fifth rotary shaft including the fifth rotary element and selectively connected to the input shaft or the fourth rotary shaft; A sixth rotary shaft including the eighth rotary element and directly connected to the output shaft; And a seventh rotary shaft including the ninth rotary element and being selectively connected to the third rotary shaft or the fifth rotary shaft. The planetary gear train of the vehicular automatic transmission may be provided.

The first planetary gear set may be a single pinion planetary gear set, wherein the first rotating element is a first sun gear, the second rotating element is a first planet carrier, and the third rotating element is a first ring gear, 2 planetary gear set is a single pinion planetary gear set, in which the fourth rotating element is composed of a second sun gear, the fifth rotating element is composed of a second planetary carrier and the sixth rotating element is composed of a second ring gear, The seventh rotary element may be a third sun gear, the eighth rotary element may be a third planetary carrier, and the ninth rotary element may be a third ring gear.

The six control elements include a first clutch selectively connecting the input shaft and the first rotation shaft; A second clutch for selectively connecting the input shaft and the fifth rotation shaft; A third clutch selectively connecting the fourth rotary shaft and the fifth rotary shaft; A fourth clutch for selectively connecting the first rotation shaft and the second rotation shaft; A fifth clutch selectively connecting the third rotary shaft and the seventh rotary shaft; And a sixth clutch that selectively connects the fifth rotary shaft and the seventh rotary shaft.

Further, the speed change stage implemented by the selective operation of the six control elements includes a forward first speed change stage by simultaneous operation of the first, third, and sixth clutches; A forward second shift stage by simultaneous operation of the first, fifth, and sixth clutches; A forward third speed change stage by simultaneous operation of the first, fourth and sixth clutches; A forward fourth shift stage by simultaneous operation of the first, second and sixth clutches; A forward fifth shift stage by simultaneous operation of the second, fourth and sixth clutches; A forward sixth shift stage by simultaneous operation of the second, fifth, and sixth clutches; A forward seventh speed change stage by simultaneous operation of the second, fourth and fifth clutches; A forward eighth speed change stage by simultaneous operation of the first, second and fifth clutches; And a reverse shift stage by simultaneous operation of the first, third, and fifth clutches.

The planetary gear train according to the embodiment of the present invention can realize the gear stages of the forward 8th speed and the reverse 1 speed by combining the three planetary gear sets of the simple planetary gear set into six control elements.

Further, the planetary gear train according to the embodiment of the present invention realizes eight forward speeds using three planetary gear sets, thereby simplifying the internal structure of the automatic transmission, thereby improving durability.

In addition, the planetary gear train according to the embodiment of the present invention can improve the fuel mileage according to the multi-shoe and improve the cruise speed of the vehicle by using the operating point of the low RPM region.

In addition, effects obtainable or predicted by the embodiments of the present invention will be directly or implicitly disclosed in the detailed description of the embodiments of the present invention. That is, various effects to be predicted according to the embodiment of the present invention will be disclosed in the detailed description to be described later.

1 is a configuration diagram of a planetary gear train according to an embodiment of the present invention.
2 is an operation table for each gear position of each control element applied to the planetary gear train according to the embodiment of the present invention.

Hereinafter, exemplary embodiments of the present invention will be described in detail with reference to the accompanying drawings, which will be readily apparent to those skilled in the art to which the present invention pertains. The present invention may, however, be embodied in many different forms and should not be construed as limited to the embodiments set forth herein.

In order to clearly illustrate the present invention, parts not related to the description are omitted, and the same or similar components are denoted by the same reference numerals throughout the specification.

In the following description, the names of the components are denoted by the first, second, etc. in order to distinguish them from each other because the names of the components are the same and are not necessarily limited to the order.

1 is a configuration diagram of a planetary gear train according to an embodiment of the present invention.

Referring to FIG. 1, a planetary gear train according to an embodiment of the present invention includes first, second, and third planetary gear sets PG1, PG2, and PG3 disposed on the same axis line, Seven output shafts TM1 to TM7 that directly connect the respective rotary elements of the first, second and third planetary gear sets PG1, PG2 and PG3 to each other, (C1 to C6), and a transmission housing (H).

The rotational power input from the input shaft IS is shifted by the complementary operation of the first, second and third planetary gear sets PG1, PG2, and PG3 and output through the output shaft OS.

The respective simple planetary gear sets are arranged in the order of the first, second and third planetary gear sets PG1, PG2, and PG3 from the engine side.

The input shaft IS is an input member, and the rotational power from the crankshaft of the engine is torque-converted through the torque converter.

The output shaft OS is an output member, which is arranged coaxially with the input shaft IS and transmits the shifted driving force to the drive shaft through the differential device.

The first planetary gear set PG1 is a single pinion planetary gear set having a first sun gear S1 which is a first rotation element N1 and a first sun gear S1 which is the first rotation element N1, A first planetary carrier PC1 which is a second rotary element N2 for supporting a first pinion P1 engaged with the first pinion P1 and a third rotary element N3 which engages with the first pinion P1 in an inner- 1 ring gear R1 as a rotation element.

The second planetary gear set PG2 is a single pinion planetary gear set that includes a second sun gear S2 that is a fourth rotary element N4, a second sun gear S2 that is the fourth rotary element N4, A second planetary carrier PC2 that is a fifth rotary element N5 that supports a second pinion P2 that meshes with the first pinion P2 and a sixth rotary element N6 that engages with the second pinion P2 in an inner- And a ring gear R2.

The third planetary gear set PG3 and the third sun gear S3 as the seventh rotary element N7 and the third sun gear S3 as the seventh rotary element N7 are arranged externally A third planetary carrier PC3 that is an eighth rotary element N8 that supports the third pinion P3 to be meshed with the third planetary carrier P3 that meshes with the third pinion P3, And a gear R3.

The first, second and third planetary gear sets PG1, PG2 and PG3 are connected such that the first rotary element N1 is directly connected to the seventh rotary element N7 and the second rotary element N2 And operates while retaining a total of seven rotary shafts TM1 to TM7 while being directly connected to the sixth rotary element N6.

The configuration of the seven rotary shafts TM1 to TM7 will be described below.

The first rotary shaft TM1 is connected to the first rotary element N1; The first sun gear S1 and the seventh rotation element N7; And a third sun gear S3), and is selectively connected to the input shaft IS.

The second rotation axis TM2 is connected to the second rotation component N2; The first planetary carrier PC1) and the sixth rotary element N6; (Second ring gear R2), and is selectively connected to the first rotation axis TM1.

The third rotary shaft TM3 is connected to the third rotary element N3; The first ring gear R1).

The fourth rotary shaft TM4 is connected to the fourth rotary element N4; (Second sun gear S2), and is directly connected to the transmission housing H to always operate as a stationary element.

The fifth rotary shaft TM5 is connected to the fifth rotary element N5; And a second planetary carrier PC2, and is selectively connected to the input shaft IS and the fourth rotation shaft TM4.

The sixth rotary shaft TM6 is connected to the eighth rotary element N8. And a third planetary carrier PC3, and is directly connected to the output shaft OS and is always operated as an output element.

The seventh rotary shaft TM7 is connected to the ninth rotary element N9; (Third ring gear R3), and is selectively connected to the third rotation axis TM3 and the fifth rotation axis TM5.

Six clutches C1, C2, C3, C4, C5, and C6, which are control elements, are disposed at a portion of the rotary shafts TM1 to TM7 selectively connected to the rotary shafts.

The arrangement positions of the six control elements (C1 to C6) will now be described.

The first clutch C1 is disposed between the input shaft IS and the first rotary shaft TM1 so that the input shaft IS and the first rotary shaft TM1 are selectively integrated.

The second clutch C2 is disposed between the input shaft IS and the fifth rotary shaft TM5 so that the input shaft IS and the fifth rotary shaft TM5 are selectively integrated.

The third clutch C3 is interposed between the fourth rotary shaft TM4 and the fifth rotary shaft TM5 so that the fourth rotary shaft TM4 and the fifth rotary shaft TM5 are selectively integrated.

The fourth clutch C4 is interposed between the first rotary shaft TM1 and the second rotary shaft TM2 so that the first rotary shaft TM1 and the second rotary shaft TM2 are selectively integrated.

The fifth clutch C5 is interposed between the third rotary shaft TM3 and the seventh rotary shaft TM7 so that the third rotary shaft TM3 and the seventh rotary shaft TM7 are selectively integrated.

The sixth clutch C6 is interposed between the fifth rotary shaft TM5 and the seventh rotary shaft TM7 so that the fifth rotary shaft TM5 and the seventh rotary shaft TM7 are selectively integrated.

The respective control elements constituted by the first, second, third, fourth, fifth and sixth clutches C1, C2, C3, C4, C5 and C6 are frictionally engaged Plate type hydraulic friction coupling unit.

2 is an operation table for each gear position of each control element applied to the planetary gear train according to the embodiment of the present invention.

As shown in FIG. 2, in the planetary gear train according to the embodiment of the present invention, three control elements are operated at respective gear positions to perform shifting.

The first, third, and sixth clutches C1, C3, and C6 are simultaneously operated at the forward first speed stage D1. The input shaft IS is interconnected with the first rotary shaft TM1 by the operation of the first clutch C1 and the fourth rotary shaft TM4 is connected to the fifth rotary shaft TM3 And the fifth rotary shaft TM5 is interconnected with the seventh rotary shaft TM7 by the operation of the sixth clutch C6. Then, while the input is being made to the first rotary shaft TM1, the fourth rotary shaft TM4 operates as a fixed element and is shifted to the first forward speed and outputted through the output shaft OS including the sixth rotary shaft TM6 .

In the forward second speed-change stage D2, the first, fifth, and sixth clutches C1, C5, and C6 operate simultaneously. The input shaft IS is interconnected with the first rotary shaft TM1 by the operation of the first clutch C1 and the third rotary shaft TM3 is connected to the seventh rotary shaft TM7 by the operation of the fifth clutch C5. And the fifth rotary shaft TM5 is interconnected with the seventh rotary shaft TM7 by the operation of the sixth clutch C6. Then, while the input is being made to the first rotary shaft TM1, the fourth rotary shaft TM4 operates as a fixed element and is shifted to the second forward speed and outputted through the output shaft OS including the sixth rotary shaft TM6 .

In the forward third speed-change stage D3, the first, fourth, and sixth clutches C1, C4, and C6 operate simultaneously. The input shaft IS is interconnected with the first rotary shaft TM1 by the operation of the first clutch C1 and the first rotary shaft TM1 is connected to the second rotary shaft TM2 And the fifth rotary shaft TM5 is interconnected with the seventh rotary shaft TM7 by the operation of the sixth clutch C6. Then, the fourth rotary shaft TM4 operates as a fixed element while being input to the first rotary shaft TM1, and is shifted to the third forward speed and output through the output shaft OS including the sixth rotary shaft TM6 .

In the forward fourth-speed gear stage D4, the first, second and sixth clutches C1, C2, and C6 operate simultaneously. The input shaft IS is interconnected with the first rotary shaft TM1 by the operation of the first clutch C1 and the input shaft IS is engaged with the fifth rotary shaft TM5 by the operation of the second clutch C2. And the fifth rotary shaft TM5 is interconnected with the seventh rotary shaft TM7 by the operation of the sixth clutch C6. In this state, the fourth rotary shaft TM4 operates as a fixed element while being input to the first rotary shaft TM1 and the fifth rotary shaft TM5, (OS).

In the forward fifth speed gear stage D5, the second, fourth, and sixth clutches C2, C4, and C6 are operated simultaneously. The input shaft IS is interconnected with the fifth rotary shaft TM5 by the operation of the second clutch C2 and the first rotary shaft TM1 is connected to the second rotary shaft TM2 And the fifth rotary shaft TM5 is interconnected with the seventh rotary shaft TM7 by the operation of the sixth clutch C6. In this state, the fourth rotary shaft TM4 operates as a fixed element while being input to the fifth rotary shaft TM5, and is shifted to the forward fifth rotary speed so as to be output through the output shaft OS including the sixth rotary shaft TM6 .

In the forward sixth-speed gear stage D6, the second, fifth, and sixth clutches C2, C5, and C6 are operated simultaneously. The input shaft IS is interconnected with the fifth rotary shaft TM5 by the operation of the second clutch C2 and the third rotary shaft TM3 is connected to the seventh rotary shaft TM7 by the operation of the fifth clutch C5. And the fifth rotary shaft TM5 is interconnected with the seventh rotary shaft TM7 by the operation of the sixth clutch C6. Then, the fourth rotary shaft TM4 operates as a fixed element while being input to the fifth rotary shaft TM5, and is shifted to the forward sixth rotary element so as to be output through the output shaft OS including the sixth rotary shaft TM6 .

At the forward seventh-speed stage D7, the second, fourth, and fifth clutches C2, C4, and C5 operate simultaneously. The input shaft IS is interconnected with the fifth rotary shaft TM5 by the operation of the second clutch C2 and the first rotary shaft TM1 is connected to the second rotary shaft TM2 And the third rotary shaft TM3 is interconnected with the seventh rotary shaft TM7 by the operation of the fifth clutch C5. Then, while the input is being made to the fifth rotary shaft TM5, the fourth rotary shaft TM4 operates as a fixed element and is shifted to the forward seventh gear to be output through the output shaft OS including the sixth rotary shaft TM6 .

In the forward 8-speed range stage D8, the first, second and fifth clutches C1, C2, and C5 operate simultaneously. The input shaft IS is interconnected with the first rotary shaft TM1 by the operation of the first clutch C1 and the input shaft IS is engaged with the fifth rotary shaft TM5 by the operation of the second clutch C2. And the third rotary shaft TM3 is interconnected with the seventh rotary shaft TM7 by the operation of the fifth clutch C5. In this state, the fourth rotary shaft TM4 operates as a fixed element while being input to the first rotary shaft TM1 and the fifth rotary shaft TM5, (OS).

And the first, third, and fifth clutches C1, C3, and C5 are operated simultaneously in the reverse shift stage REV. The input shaft IS is interconnected with the first rotary shaft TM1 by the operation of the first clutch C1 and the fourth rotary shaft TM4 is connected to the fifth rotary shaft TM3 And the third rotary shaft TM3 is interconnected with the seventh rotary shaft TM7 by the operation of the fifth clutch C5. The fourth rotary shaft TM4 operates as a fixed element while being input to the first rotary shaft TM1 and is shifted backward and output through the output shaft OS including the sixth rotary shaft TM6.

As described above, in the planetary gear train according to the embodiment of the present invention, the three planetary gear sets PG1, PG2 and PG3 are connected to six clutches C1, C2, C3, C4, C5, It is possible to realize the forward speeds of the forward 8th speed and the reverse 1 speed.

In addition, the planetary gear train according to the embodiment of the present invention realizes eight forward speeds using three planetary gear sets PG1, PG2, and PG3, thereby improving the durability by simplifying the internal structure of the automatic transmission .

In addition, the planetary gear train according to the embodiment of the present invention can improve the fuel mileage according to the multi-shoe and improve the cruise speed of the vehicle by using the operating point of the low RPM region.

It will be apparent to those skilled in the art that various modifications and variations can be made in the present invention without departing from the spirit or scope of the invention as defined in the appended claims. It will be understood that the invention may be varied and varied without departing from the scope of the invention.

First, second, third, fourth, fifth and sixth clutches C1, C2, C3, C4, C5,
PG1, PG2, PG3 ... First, second and third planetary gear sets
S1, S2, S3 ... First, second, and third sun gear
PC1, PC2, PC3 ... First, second and third planetary carriers
R1, R2, R3 ... First, second and third ring gears
IS ... input shaft
OS ... Output shaft
TM1, TM2, TM3, TM4, TM5, TM6, TM7 ... First, second, third, fourth, fifth, sixth,

Claims (10)

An input shaft receiving power of the engine;
An output shaft for outputting the shifted power;
A first planetary gear set having first, second and third rotating elements;
A second planetary gear set having fourth, fifth and sixth rotating elements;
A third planetary gear set having seventh, eighth and ninth rotary elements; And
And six control elements disposed at a portion that selectively connects the rotary element and the rotary element,
A first rotating shaft including the first rotating element and the seventh rotating element and selectively connected to the input shaft;
A second rotating shaft including the second rotating element and the sixth rotating element, the second rotating shaft being selectively connected to the first rotating shaft;
A third rotating shaft including the third rotating element;
A fourth rotary shaft including the fourth rotary element and directly connected to the transmission housing;
A fifth rotary shaft including the fifth rotary element and selectively connected to the input shaft or the fourth rotary shaft;
A sixth rotary shaft including the eighth rotary element and directly connected to the output shaft; And
And a seventh rotary shaft including the ninth rotary element and selectively connected to the third rotary shaft or the fifth rotary shaft,
The six control elements
A first clutch selectively connecting the input shaft and the first rotation shaft;
A second clutch for selectively connecting the input shaft and the fifth rotation shaft;
A third clutch selectively connecting the fourth rotary shaft and the fifth rotary shaft;
A fourth clutch for selectively connecting the first rotation shaft and the second rotation shaft;
A fifth clutch selectively connecting the third rotary shaft and the seventh rotary shaft; And
And a sixth clutch that selectively connects the fifth rotary shaft and the seventh rotary shaft. The method according to claim 1,
Wherein the first planetary gear set is a single pinion planetary gear set wherein the first rotating element is a first sun gear, the second rotating element is a first planet carrier, and the third rotating element is a first ring gear,
Wherein the second planetary gear set is a single pinion planetary gear set, wherein the fourth rotating element is composed of a second sun gear, the fifth rotating element is composed of a second planetary carrier and the sixth rotating element is composed of a second ring gear,
Wherein the third planetary gear set is a single pinion planetary gear set, and the planetary gear set of the automatic transmission for a vehicle, in which the seventh rotary element is the third sun gear, the eighth rotary element is the third planetary carrier, Train. delete The method according to claim 1,
The speed change stages implemented by the selective operation of the six control elements
A forward first speed change stage by simultaneous operation of the first, third and sixth clutches;
A forward second shift stage by simultaneous operation of the first, fifth, and sixth clutches;
A forward third speed change stage by simultaneous operation of the first, fourth and sixth clutches;
A forward fourth shift stage by simultaneous operation of the first, second and sixth clutches;
A forward fifth shift stage by simultaneous operation of the second, fourth and sixth clutches;
A forward sixth shift stage by simultaneous operation of the second, fifth, and sixth clutches;
A forward seventh speed change stage by simultaneous operation of the second, fourth and fifth clutches;
A forward eighth speed change stage by simultaneous operation of the first, second and fifth clutches; And
And a reverse shift stage by simultaneous operation of the first, third and fifth clutches. delete delete delete delete delete delete

Images